JP4553636B2 - Lock-up device for fluid torque transmission device - Google Patents

Description

The present invention, a lockup device for a fluid-type torque transmission device, in particular, piston relates lockup device for pressing themselves to the front cover.

  The torque converter is a device that transmits torque from the engine to the transmission side via an internal working fluid. The torque converter mainly includes a front cover to which torque from the engine is input, and a fluid chamber fixed to the transmission side of the front cover. An impeller that forms a shaft, a turbine that is arranged to face the engine side of the impeller and outputs torque to the transmission side, and an operation that is arranged between the inner peripheral portion of the impeller and the inner peripheral portion of the turbine and that travels from the turbine to the impeller And a stator that rectifies the flow of fluid.

  The lockup device is disposed in a space between the turbine and the front cover, and is a device for directly transmitting torque from the front cover to the turbine by mechanically connecting the front cover and the turbine. The lockup device includes, for example, a disk-like piston that is connected by being pressed against the friction surface of the front cover, and an elastic connection mechanism that transmits torque between the piston and the turbine.

  In such a lock-up device, the piston has a frictional connection portion that can be frictionally connected to the front cover on the outer peripheral portion. The piston divides the space between the front cover and the turbine into a first hydraulic chamber and a second hydraulic chamber on the front cover side, and the axial direction is determined by the differential pressure between the first hydraulic chamber and the second hydraulic chamber. (For example, refer to Patent Document 1).

Next, the operation of the lockup device will be described. At the time of torque transmission by the fluid, hydraulic oil is supplied from the center side to the first hydraulic chamber, and the hydraulic oil flows to the outer peripheral side and further flows into the fluid hydraulic chamber of the torque converter. Therefore, the piston is separated from the front cover in the axial direction (clutch release state). Subsequently, during the lockup coupling operation, the hydraulic circuit is switched, and the hydraulic oil in the first hydraulic chamber is discharged to the inner peripheral side. For this reason, the hydraulic pressure in the first hydraulic chamber becomes lower than the hydraulic pressure in the second hydraulic chamber, and the piston approaches the front cover side. As a result, the friction coupling portion of the piston is strongly pressed against the front cover (clutch coupling state).
JP-A-11-63151

  The adoption of the lock-up device has the effect of improving the fuel efficiency and improving the engine brake effect, which has been regarded as a drawback of conventional automatic vehicles. Furthermore, with the shift to electronic control of transmission control, there is an increasing tendency to use lockup in a wide range, such as lockup control from the first gear and slip-up slip control. In particular, attempts have been made to improve the effectiveness of the engine brake by operating a lock-up when using the engine brake.

However, if the lock-up operation region is expanded to the reverse drive (state where the output rotation speed is higher than the input rotation speed), the problem of deterioration of the operation response of the lock-up device becomes significant. In general, actuation responsiveness of the quality of the lock-up device, after switching to lock-up circuit, the lock-up clutch is determined by the time until the fastening. At the time of reverse driving, the direction of the flow of the hydraulic oil is reversed in the torque converter, and the hydraulic oil flows from the outer peripheral portion of the turbine to the impeller, and flows from the inner peripheral portion of the impeller to the turbine through the stator. For this reason, during reverse driving, hydraulic oil flows from the space between the turbine and the front cover into the torus through the outer periphery of the turbine and the impeller, so that the hydraulic pressure in the second hydraulic chamber tends to be low. For this reason, in general, the lockup operation responsiveness is not good during reverse driving.

  In particular, it can be considered that it takes too much time to decrease the hydraulic pressure in the first hydraulic chamber, which is one cause of the decrease in the lockup operation response. In the first hydraulic chamber, when the discharge of the working fluid is started, the working fluid gradually moves toward the center side (inward in the radial direction) while flowing in the rotational direction (turning around). Therefore, it takes a certain time to discharge the working fluid.

  An object of the present invention is to improve lockup operation responsiveness during reverse driving in a lockup device in which a piston is connected to a front cover.

The lock-up device according to claim 1 is arranged to face the impeller in the fluid chamber, a front cover to which torque is input, an impeller which is fixed to the front cover and forms a fluid chamber filled with a working fluid. A fluid torque transmission device including a turbine is provided with a piston. The piston is arranged so as to divide the space between the front cover and the turbine into a first hydraulic chamber on the front cover side and a second hydraulic chamber on the turbine side, and the front pressure is determined by the differential pressure between the first and second hydraulic chambers. It can be connected to and released from the cover. The piston is a plate-like member and has a plurality of protrusions extending from the inner peripheral side to the outer peripheral side on the surface of the first hydraulic chamber. The protrusion has a linear rotation direction front side and a rotation direction rear side, and an arc-shaped outer periphery and inner periphery. The rear side in the rotation direction overlaps with the straight line Ls connecting the inner peripheral end and the rotation center, or the rear side in the rotation direction is inclined so that the outer peripheral end is located on the rear side in the rotation direction with respect to the straight line Ls. Further, the front side in the rotation direction overlaps with a straight line Lp connecting the inner peripheral end and the rotation center, or the front side in the rotation direction is inclined so that the outer peripheral end is located on the rear side in the rotation direction with respect to the straight line Lp. . On the other hand, when the front side in the rotation direction is inclined so as to be positioned on the front side in the rotation direction with respect to the straight line Lp, the action of pushing the fluid forward in the rotation direction to increase the rotation speed is increased. Increases and lock-up operation responsiveness deteriorates. Then, assuming that the circumferential length of the outer periphery is S ₁ and the circumferential length of the inner periphery is S ₂ , the relationship of S ₂ <S ₁ is established.

  In this lock-up device, the piston moves in the axial direction due to a change in hydraulic pressure, and for example, presses itself against the front cover to engage or disengage from the clutch. During the lockup connection operation, the working fluid in the first hydraulic chamber is discharged to the center side. At this time, the working fluid tends to gradually move toward the center while flowing in the rotation direction, but when it collides with each protrusion, it is guided radially inward along the protrusion. Accordingly, the hydraulic oil is quickly discharged. As a result, the pressure drop in the first hydraulic chamber is promoted, and the lockup operation response during reverse driving is improved.

The rear side in the rotation direction overlaps the straight line Ls connecting the inner peripheral end and the rotation center, or the rear side in the rotation direction is inclined so that the outer peripheral end is located on the rear side in the rotation direction with respect to the straight line Ls. the pressure drop occurring in the rotational direction after the side, the fluid is drawn from the rear to the projections, Ru is guided on the inner peripheral side along the rear edge.

The lock-up device according to 請 Motomeko 2, in claim 1, and the radius of the outer periphery and r _1, the relationship of _{S 1 ≦ (2πr 1) /} 8 is satisfied.

In the lockup device according to a third aspect , the relationship of S ₂ <(2πr ₂ ) / 8 is established, where the radius of the inner periphery is r ₂ in the first or second aspect .

In the lock-up device according to claim 4, in claim 2 or 3, S ₂ is more than 6mm.

In the lockup device according to a fifth aspect , in any one of the first to fourth aspects, the front side in the rotational direction has a front side wall surface that forms an angle βp with respect to a surface other than the protrusion. The rear side in the rotation direction has a rear side wall surface that forms an angle βs with respect to a surface other than the protrusions. The relationship βp ≦ βs is established.

  In this lockup device, since the angle βs of the rear side in the rotational direction is sufficiently large, the pressure drop generated on the rear side in the rotational direction becomes large.

In the lockup device for the fluid torque transmission device according to the sixth aspect , the relationship βp <βs is established in the fifth aspect .

  In this lockup device, since the angle βs of the rear side in the rotational direction is sufficiently large, the pressure drop generated on the rear side in the rotational direction becomes large.

In the lockup device according to a seventh aspect , in the fifth or sixth aspect , βs is in a range of 80 to 100 degrees.

  In this lockup device, since the angle βs of the rear side in the rotational direction is sufficiently large, the pressure drop generated on the rear side in the rotational direction becomes large.

The lockup device according to claim 8 is arranged to face the impeller in the fluid chamber, a front cover to which torque is input, an impeller that is fixed to the front cover and forms a fluid chamber filled with a working fluid. A fluid torque transmission device including a turbine is provided with a piston. The piston is arranged so as to divide the space between the front cover and the turbine into a first hydraulic chamber on the front cover side and a second hydraulic chamber on the turbine side, and the front pressure is determined by the differential pressure between the first and second hydraulic chambers. It can be connected to and released from the cover. The piston is a plate-like member and has a plurality of protrusions extending from the inner peripheral side to the outer peripheral side on the surface of the first hydraulic chamber. The protrusion has a linear rotation direction front side and a rotation direction rear side, and an arc-shaped outer periphery and inner periphery. The front side in the rotation direction has a front side wall surface that forms an angle βp with respect to a surface other than the protrusions. The rear side in the rotation direction has a rear side wall surface that forms an angle βs with respect to a surface other than the protrusions. The relationship βp < βs is established.

  In this lock-up device, the piston moves in the axial direction due to a change in hydraulic pressure, and for example, presses itself against the front cover to engage the clutch, or away from the clutch to release the clutch. During the lockup connection operation, the working fluid in the first hydraulic chamber is discharged to the center side. At this time, the working fluid gradually moves toward the center while flowing in the rotational direction, but when it collides with each protrusion, it is guided radially inward along the protrusion. Accordingly, the hydraulic oil is quickly discharged. As a result, the pressure drop in the first hydraulic chamber is promoted, and the lockup operation responsiveness during reverse driving is improved.

In particular, the relationship βp <βs is established, and the angle βs of the rear side in the rotational direction is sufficiently large, so that the pressure drop generated on the rear side in the rotational direction becomes large.

In the lockup device according to a ninth aspect , in the eighth aspect , βs is in a range of 80 to 100 degrees.

  In this lockup device, since the angle βs of the rear side in the rotational direction is sufficiently large, the pressure drop generated on the rear side in the rotational direction becomes large.

  In the lockup device according to the present invention, the lockup operation responsiveness during reverse driving is improved by the plurality of protrusions.

1. Structure of Torque Converter Hereinafter, an embodiment of the present invention will be described with reference to the drawings.

  FIG. 1 shows a torque converter 1 as an embodiment of the present invention. The torque converter 1 is employed in a vehicle. 1 is the rotation axis of the torque converter 1. In FIG. 1, the torque converter 1 forms a hydraulic oil chamber by a front cover 2 and an impeller shell 9 fixed to an outer peripheral side protruding portion 8 of the front cover 2. The front cover 2 can be attached to engine-side components (not shown) so that torque from the engine can be input. A plurality of impeller blades 10 are fixed inside the impeller shell 9. An impeller 3 is constituted by the impeller shell 9 and the impeller blade 10. A turbine 4 is disposed at a position facing the impeller 3 in the hydraulic oil chamber. The turbine 4 includes a turbine shell 11 and a plurality of turbine blades 12 fixed on the turbine shell 11. An inner peripheral end portion of the turbine shell 11 is fixed to a flange 15 of the turbine hub 13 via a rivet 14. The turbine hub 13 has a spline groove 20 that engages with a main drive shaft (not shown) of the transmission on the inner periphery.

  A stator 5 is disposed between the inner periphery of the impeller 3 and the inner periphery of the turbine 4. The stator 5 adjusts the direction of hydraulic fluid returned from the turbine 4 to the impeller 3 and is supported by a fixed shaft (not shown) via a one-way clutch 6.

2. Structure of Lock-Up Clutch The lock-up clutch 7 is a device that is disposed in a space between the front cover 2 and the turbine 4 and mechanically connects the front cover 2 and the turbine 4. The lockup clutch 7 mainly includes a piston 22 and an elastic coupling mechanism 40 for elastically coupling the piston 22 to the turbine 4.

  The piston 22 is a disk-shaped member, and divides the space between the front cover 2 and the turbine shell 11 into a first hydraulic chamber 36 on the front cover 2 side and a second hydraulic chamber 37 on the turbine 4 side. Are arranged as follows. The piston 22 is made of a thin metal plate. The piston 22 has an inner peripheral cylindrical portion 23 extending toward the transmission side on the inner peripheral side. The inner peripheral cylindrical portion 23 is supported on the outer peripheral surface 19 of the cylindrical portion 16 formed on the outermost periphery of the flange 15 of the turbine hub 13 so as to be relatively movable in the axial direction and the circumferential direction. That is, the inner peripheral surface 25 of the inner peripheral cylindrical portion 23 is in contact with the outer peripheral surface 19 of the cylindrical portion 16. An annular groove is formed on the outer peripheral surface 19 of the cylindrical portion 16 at an intermediate position in the radial direction. A seal ring 18 is disposed in the annular groove, and the seal ring 18 is in contact with the inner peripheral surface 25 of the inner peripheral protrusion 23. Thus, the seal ring 18 seals the inner peripheral portions of the first hydraulic chamber 36 and the second hydraulic chamber 37.

  An outer peripheral cylindrical portion 24 extending to the transmission side is formed on the outer peripheral portion of the piston 22. An annular friction facing 35 (friction engaging portion) is stretched on the engine side in the outer peripheral portion of the piston 22. The friction facing 35 is opposed to an annular flat friction surface 2 a formed on the inner periphery of the front cover 2. By the engagement between the friction facing 35 and the front cover friction surface 2a, the outer peripheral portions of the first hydraulic chamber 36 and the second hydraulic chamber 37 are sealed.

  A plurality of protrusions 41 are formed in the intermediate portion in the radial direction of the piston 22. The protrusion 41 is a portion formed by drawing, and is a rib protruding toward the axial front cover 2 side. As shown in FIG. 2, the protrusions 41 are arranged in a line in the circumferential direction and extend linearly in the radial direction. That is, the protrusion 41 is formed radially in the piston 22. Due to the above-described protrusion 41, the surface of the piston 22 on the axial front cover 2 side has a generally flat surface 42 in the circumferential direction and a protrusion 41 slightly protruding in the axial direction from the surface 42. They are alternately arranged in the circumferential direction. The protrusions 41 are arranged at equal intervals in the circumferential direction.

  The shape of the protrusion 41 will be described in detail with reference to FIG. The protrusion 41 extends from the inner peripheral side to the outer peripheral side on the surface on the first hydraulic chamber 36 side. The protrusion 41 includes a linear rotation direction front side 51 and a rotation direction rear side 52, and an arcuate outer periphery 53 and an inner periphery 54.

  The rotation direction front side 51 is the rotation direction front side, that is, the pressure side. More specifically, the outer peripheral end 51b is inclined by αp degrees so that the outer peripheral end 51b is located on the rear side in the rotation direction with respect to the straight line Lp connecting the inner peripheral end 51a and the rotation center O. The rotation direction front side 51 may overlap the straight line Lp. That is, the rotation direction front side 51 is not positioned on the front side in the rotation direction on the outer peripheral side compared to the inner peripheral side.

  The rear side 52 in the rotation direction is the rear side in the rotation direction, that is, the suction side. More specifically, the rotational direction rear side 52 is inclined by αs degrees so that the outer peripheral end 52b is located on the rear side in the rotational direction with respect to the straight line Ls connecting the inner peripheral end 52a and the rotational center O. The rotation direction front side 52 may overlap the straight line Ls. That is, the rear side 52 in the rotational direction is not positioned on the front side in the rotational direction on the outer peripheral side compared to the inner peripheral side.

Since αp ≦ αs, the circumferential length S ₁ of the outer periphery 53 is longer than the circumferential length S ₂ of the inner periphery 54.

When the radius of the outer periphery 53 is r ₁ , the relationship S ₁ ≦ (2πr ₁ ) / 8 is established. When the radius of the inner periphery 54 is r ₂ , the relationship S ₂ <(2πr ₂ ) / 8 is established. Circumferential length S ₂ of the inner periphery 54 is 6mm or more.

As shown in FIG. 4, the rotation direction front side 51 has a front side wall surface 57 that forms an angle βp with respect to the surface 42 other than the protrusions. The rear side in the rotation direction has a rear side wall surface 58 that forms an angle βs with respect to a surface other than the protrusions. More precisely, the angles βp and βs are angles formed by the front side wall surface 57 and the rear side wall surface 58 with respect to the surface 42 in the longitudinal cross section in the circumferential direction. In this embodiment, the angle .beta.p is 52 degrees, the angle .beta.s is 65 degrees, you are satisfied .beta.p <.beta.s relationship.

Na us, in another embodiment shown in FIG. 5, .beta.s is 90 degrees. βs is preferably in the range of 80 to 100 degrees.

  The elastic coupling mechanism 40 is disposed between the piston 22 and the turbine 4, more specifically, between the outer peripheral portion of the piston 22 and the outer peripheral portion of the turbine shell 11. The elastic coupling mechanism 40 includes a retaining plate 27 as a drive-side member, a driven plate 33 as a driven-side member, and a plurality of coil springs 32 disposed between the plates 27 and 33. The retaining plate 27 is an annular plate member disposed on the outer peripheral side of the piston 22, that is, on the inner peripheral side of the outer peripheral side tubular part 24. The inner peripheral portion of the retaining plate 27 is fixed to the piston 22 by a plurality of rivets (not shown). The retaining plate 27 is a member for holding the coil spring 32 and for transmitting torque by engaging with both sides of the coil spring 32 in the circumferential direction. The retaining plate 27 has holding portions 28 and 29 that respectively support the outer peripheral side and the inner peripheral side of the plurality of coil springs 32 arranged in the circumferential direction. The inner peripheral holding portion 29 is formed by being cut and raised from the disc-shaped portion of the retaining plate 27. Further, the retaining plate 27 has engaging portions 30 for supporting both sides of each coil spring 32 in the circumferential direction. The driven plate 33 is an annular plate member fixed to the rear surface of the outer peripheral portion of the turbine shell 11. The driven plate 33 is formed with a plurality of claw portions 34 extending to the engine side at a plurality of locations in the circumferential direction. The claw portions 34 are engaged with both ends of each coil spring 32 in the circumferential direction. Thereby, the torque from the retaining plate 27 is transmitted to the driven plate 33 via the coil spring 32.

3. Operation of Torque Converter The operation of the torque converter 1 will be described. When torque is transmitted from the engine to the front cover 2, the impeller 3 rotates together with the front cover 2. Thereby, hydraulic fluid flows from the impeller 3 to the turbine 4 to rotate the turbine 4. The torque of the turbine 4 is transmitted to a main drive shaft (not shown). At this time, hydraulic oil is supplied into the first hydraulic chamber 36 from the inner peripheral side. The hydraulic oil flows radially outward in the first hydraulic chamber 36, further flows toward the axial transmission side, and finally flows into the fluid working chamber (torus). Therefore, the piston 22 has moved most to the axial turbine 4 side, and the friction facing 35 of the piston 22 is separated from the friction surface 2 a of the front cover 2. At this time, the hydraulic oil in the fluid working chamber is discharged to the outside through the space between the inner peripheral portions of the turbine 4 and the stator 5.

  At the time of lockup connection, the hydraulic circuit is switched, and the hydraulic oil in the first hydraulic chamber 36 is drained from the inner periphery. Therefore, the hydraulic pressure in the first hydraulic chamber 36 is lower than the hydraulic pressure in the second hydraulic chamber 37. As a result, the piston 22 moves to the front cover 2 side, and the friction facing 35 is strongly pressed against the friction surface 2 a of the front cover 2. At this time, the hydraulic oil is supplied to the fluid working chamber through the impeller 3 and the inner peripheral portion of the stator 5.

  The movement operation of the piston 22 will be described in further detail. Note that the hydraulic oil in the first hydraulic chamber 36 shown in FIG. 1 starts to move gradually toward the inner periphery side while moving substantially in the rotational direction, similar to the conventional example, when draining is started. However, in this embodiment, since the piston 22 is provided with a plurality of protrusions 41, the hydraulic oil F on the surface of the piston 22 collides with the protrusions 41 on the rotation direction side, and on the inner peripheral side. The direction can be changed (to the center side). In other words, the hydraulic fluid on the suction side of each projecting portion 41 is directed along the projecting portion 41 toward the inner peripheral side. For this reason, hydraulic fluid moves to a radial inside rapidly. Since the hydraulic oil discharge time is shortened in this way, the hydraulic pressure drop time of the first hydraulic chamber 36 is shortened. As described above, the operation responsiveness of the piston 22 is improved, and sufficient operation responsiveness can be obtained even during reverse driving.

  Since the rear side 5 in the rotation direction overlaps with the straight line Ls connecting the inner peripheral end 52a and the rotation center O, or the outer peripheral end 52b is inclined so as to be located on the rear side in the rotation direction with respect to the straight line Ls. Due to the pressure drop generated in the rear side 52 in the rotation direction, the fluid is attracted to the protrusion 41 from the rear and guided to the inner peripheral side along the rear side 52.

  The rotation direction front side 51 has a front side wall surface 57 that forms an angle βp with respect to the surface 42, and the rotation direction rear side 52 has a rear side wall surface 58 that forms an angle βs with respect to the surface 42, and βp Since the relationship of <βs is established, the angle βs of the rear side 52 in the rotation direction is sufficiently large, and the pressure drop generated on the rear side 52 in the rotation direction is increased.

  On the contrary, when the front end of the rotation direction is inclined so that the outer peripheral end is located on the front side of the rotation direction with respect to the straight line connecting the inner peripheral end and the rotation center O (for example, the outer peripheral side of the rib is more than the inner peripheral side). (If it is on the front side in the direction of rotation), the action of pushing the fluid forward in the direction of rotation to increase its rotational speed is increased, so that the rotational speed of the fluid is increased, thereby increasing the centrifugal force, resulting in the The pressure of the clutch facing portion is increased, and as a result, the effect of preventing the decrease in the clearance between the clutch facing and the front cover is exhibited. Further, when the rear end in the rotation direction is inclined such that the outer peripheral end is located on the front side in the rotation direction with respect to the straight line connecting the inner peripheral end and the rotation center O (for example, the rib is inclined in the rotation direction). (When it has a cross-sectional shape), the pressure drop that occurs on the rear side in the rotational direction is reduced, and the fluid is less likely to be attracted to the protrusion from the rear. Therefore, also in this case, it is difficult to obtain the excellent effect of the present invention.

  Regarding the responsiveness of the lockup ON, the conventional lockup device and the lockup device according to the present invention were compared. This measurement was performed on the same product except for the lock-up device, that is, the lock-up piston and damper.

  The performance of the torque converter was compared between the conventional product (without ribs) and the product of the present invention (with ribs). FIG. 6 shows the case where the input rotation speed is 1500 rpm and the speed ratio is 0.2 and 0.4, the input rotation speed is 2000 rpm and the speed ratio is 0.2 and 0.4, that is, four cases. The variation range of the capacity coefficient with respect to the cutting allowance was measured. The cutting allowance was set to be in the vicinity of 0.3 mm, 0.5 mm, and 0.7 mm. The cutting allowance is a clearance between the friction facing of the piston and the friction surface of the front cover. The speed ratios 0.2 and 0.4 are both low speed ratio areas.

  As is apparent from FIG. 6, the product of the present invention (with ribs) has a higher capacity coefficient than the conventional product (without ribs). The fact that the three elements of the torque converter are the same and the capacity coefficient is high is a result of an increase in the pressing force of the lockup piston against the front cover. That is, in the above experimental example, the hydraulic pressure between the front cover and the piston is lower in the product of the present invention than in the conventional product, and the pressing force of the piston against the front cover is increased. In general, when the inlet / outlet hydraulic pressures of both devices are equal in the torque converter region, the responsiveness (OFF → ON) of lockup ON is improved when the hydraulic pressure in the hydraulic chamber between the front cover and the piston is lower. Therefore, the lockup response of the present invention is improved.

  Furthermore, changes over time in the hydraulic pressure and torque waveforms related to the responsiveness of lockup were measured with the conventional product and the product of the present invention. FIG. 7 shows the results, and FIG. 8 shows each measurement site of the flow of hydraulic oil and responsiveness data. The lock-up ON response time is the time from when the hydraulic signal is switched until the torque starts to be generated.

  As is apparent from FIG. 7, the product of the present invention has a faster lock-up ON response than the conventional product. In the torque converter area, the front cover side hydraulic pressure (the hydraulic pressure in the first hydraulic chamber 36) is lower than that of the conventional product in the invention of the present application, so that the front cover side hydraulic pressure (first hydraulic pressure) is switched to the lock-up ON state. Regarding the hydraulic pressure of the chamber 36, the product of the present invention is lower than the conventional product. On the other hand, when the lock-up piston starts to move, in the first hydraulic chamber 36 of the present invention product, the discharge of the working fluid to the center portion becomes smooth, and the front cover side hydraulic pressure becomes higher than that of the conventional product. However, since the hydraulic pressure in the second hydraulic chamber 37 is estimated to be equal to or higher than that of the conventional product, and the working fluid is discharged in a short time, the responsiveness of the lockup ON is improved.

  As mentioned above, although embodiment of this invention was described based on drawing, a specific structure is not restricted to these embodiment, It can change in the range which does not deviate from the summary of invention.

  In the embodiment, the present invention is applied to the torque converter, but may be applied to other fluid type torque transmission devices.

  Further, the shape and size of the protrusion, the relationship with other members, and the like are not limited to the embodiment.

1 is a schematic vertical sectional view of a torque converter in which an embodiment of the present invention is employed. The partial top view for demonstrating the flow of the hydraulic fluid in the 1st hydraulic chamber at the time of lockup connection operation | movement. The detailed top view of a projection part. The schematic diagram which shows the three-dimensional shape of a projection part. The schematic diagram which shows the three-dimensional shape of the projection part of a modification. The graph which compared the output capacity coefficient with the conventional product and the present invention product. The graph which compared the lockup responsiveness of the conventional product and this invention product. The schematic diagram which shows a hydraulic pressure measurement site | part.

1 Torque converter (fluid torque transmission device)
2 Front cover 2a Friction surface 3 Impeller 4 Turbine 7 Lock-up clutch (lock-up device)
22 Piston 41 Projection

Claims (9)

A hydrodynamic torque transmission including a front cover to which torque is input, an impeller that is fixed to the front cover and forms a fluid chamber filled with a working fluid, and a turbine that is disposed in the fluid chamber so as to face the impeller. A device lock-up device,
The space between the front cover and the turbine is arranged so as to be divided into a first hydraulic chamber on the front cover side and a second hydraulic chamber on the turbine side, and the differential pressure between the first and second hydraulic chambers A piston that can be connected to and released from the front cover by
The piston is a plate-like member, and has a plurality of protrusions extending from the inner peripheral side to the outer peripheral side on the surface on the first hydraulic chamber side,
The protrusion has a linear rotation direction front side and a rotation direction rear side, and an arc-shaped outer periphery and inner periphery,
The rear side in the rotation direction overlaps the straight line Ls connecting the inner peripheral end and the rotation center, or the rear side in the rotation direction is inclined so that the outer peripheral end is located on the rear side in the rotation direction with respect to the straight line Ls. And
The rotation direction front side is overlapped with a straight line Lp connecting the inner peripheral end and the rotation center, or the rotation direction front side is inclined so that the outer peripheral end is located on the rear side in the rotation direction with respect to the straight line Lp. And
When the circumferential length of the outer periphery is S _{1 and} the circumferential length of the inner periphery is S ₂ , the relationship of S ₂ <S ₁ is established.
A lockup device for a fluid torque transmission device. And the radius of the outer periphery and _{r 1, S 1 ≦ (2πr} 1) / 8 relationship holds the lock-up device of the hydrodynamic torque transmitting device according to claim 1. When the radius around the said and _{r 2, S 2 <(2πr} 2) / 8 relationship holds the lock-up device of the hydrodynamic torque transmitting device according to claim 1 or 2. S ₂ is more than 6mm, the lockup device of the hydrodynamic torque transmitting device according to claim 2 or 3. The rotation direction front side has a front side wall surface that forms an angle βp with respect to a surface other than the protrusion,
The rear side in the rotation direction has a rear side wall surface that forms an angle βs with respect to a surface other than the protrusion,
The lockup device for a fluid torque transmission device according to any one of claims 1 to 4 , wherein a relationship of βp ≦ βs is established. The lockup device for a fluid torque transmission device according to claim 5 , wherein a relationship of βp <βs is established. The lockup device for a fluid torque transmission device according to claim 5 or 6 , wherein βs is in a range of 80 to 100 degrees. Fluid type torque transmission including a front cover to which torque is input, an impeller that is fixed to the front cover and forms a fluid chamber filled with a working fluid, and a turbine that is disposed in the fluid chamber so as to face the impeller. A device lock-up device,
The space between the front cover and the turbine is arranged so as to be divided into a first hydraulic chamber on the front cover side and a second hydraulic chamber on the turbine side, and the differential pressure between the first and second hydraulic chambers A piston that can be connected to and released from the front cover by
The piston is a plate-like member, and has a plurality of protrusions extending from the inner peripheral side to the outer peripheral side on the surface on the first hydraulic chamber side,
The protrusion has a linear rotation direction front side and a rotation direction rear side, and an arc-shaped outer periphery and inner periphery,
The rotation direction front side has a front side wall surface that forms an angle βp with respect to a surface other than the protrusion,
The rear side in the rotation direction has a rear side wall surface that forms an angle βs with respect to a surface other than the protrusion,
The relationship βp <βs holds.
A lockup device for a fluid torque transmission device. The lockup device for a fluid torque transmission device according to claim 8 , wherein βs is in a range of 80 to 100 degrees.

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